ES2770048T3 - Control device for a pressurized fluid supply - Google Patents

Abstract

Distributor consisting of a device for controlling the supply of fluid under pressure, consisting of a body comprising an internal diameter of the longitudinal axis (X), a mobile device (206) suitable for sliding within the internal diameter, at least one feeding hole (214) made in the body and arranged laterally with respect to the longitudinal axis (X), at least one evacuation hole (216) made in the body laterally with respect to the longitudinal axis (X), the equipment being mobile ( 206) suitable for sliding between at least a first communication interruption position between the feed port (214) and the evacuation port (216) and a second position of communication between the feed port (214) and the evacuation hole (216), means for returning the mobile equipment to the first position, the mobile equipment (206) comprising a lateral surface intended to cooperate with the internal diameter of the shaft. watertight or substantially watertight, at least one groove (226) in the lateral surface of the mobile equipment (206), said groove (226) being in permanent communication with the feed orifice (214), the mobile equipment (206) comprising at least one housing (232) extending parallel to the longitudinal axis (X) and of an element (234) slidably mounted in said housing (232), said housing (232) being in permanent communication with said groove (226) such that one end of said element (234) is in contact with the fluid under pressure and wherein the element (234) is fixed with respect to the body at least in a direction opposite to the direction of movement of the mobile equipment (226) of the first position towards the second position, said distributor also consisting of external actuation means (237) suitable for moving the mobile equipment (206) to an open position regardless of the pressure level in the throat (226), it consists nd said actuating means (237) of a magnetic core (238) and a solenoid (240) suitable for moving the magnetic core (238) along the longitudinal axis (X), where the mobile equipment consists of a drawer of distribution (206) comprising the groove (226), a pusher (244) and the magnetic core (238), the pusher (244) being in one piece with the dispensing drawer (206) and being arranged between the distribution (206) and the magnetic core (238), said magnetic core (238) being axially integral with the distribution box (206), where the housing is formed in the magnetic core (238) and where the distribution box (206) and the pusher (244) consist of a passage (250) for supplying the fluid under pressure to the housing (232) in the magnetic core (238).

Description

DESCRIPTION

Control device for a pressurized fluid supply

Technical field and prior art

The present invention relates to a control device for supplying a system with a pressurized fluid, for example, a control device for regulating oil pressure in a heat engine.

A hydraulic valve allows fluid to transfer from one path to another path when the fluid reaches a pressure threshold, called opening pressure. The valve is arranged between a supply path for the pressurized fluid and a path for evacuating the fluid towards the system to be fed. It consists of a valve body comprising an inside diameter, a piston or plug fitted with a watertight or substantially watertight slide on the inside diameter of the valve body, a valve seat against which the piston rests in the valve closed position , and a spring that returns the piston against the valve seat. The valve opening pressure level is determined by the spring return force. The valve seat is arranged between the fluid supply path and the fluid transfer path. When the piston is detached from the valve seat, the two ways are in communication; otherwise, they are isolated from each other.

The return spring force is a function of the section of the piston that sees the hydraulic pressure. A highly stiff spring, which therefore has a high return force, may therefore be necessary.

In addition, in the external drive control device, also called distributors, the two-way communication is carried out, for example, by means of a magnetic core displaced by the supply of a coil and not by the direct action of pressure on the piston. DE19949234 A1 describes such a dispenser. It may be interesting to have a distributor that is to some extent directly sensitive to this pressure.

Disclosure of the invention

Consequently, the objective of the present invention is to offer a device for controlling the supply of fluid under pressure that offers a new structure that allows, in the case of a hydraulic valve, to implement means of return of reduced force and in the case of a distributor, have a certain direct sensitivity to pressure.

The aforementioned objective is achieved by the distributor according to claim 1, which consists of a fluid supply control device consisting of a body, a mobile equipment of which at least part is suitable for sliding within the body, comprising the body at least a first lateral hole for feeding pressurized fluid and at least a first lateral hole for evacuating pressurized fluid, means for closing the mobile equipment in return, the mobile equipment consisting of a throat of the mobile equipment in its Lateral surface in permanent communication with the first lateral feeding hole. An element is movably mounted in a housing of the mobile equipment and is fixed with respect to the body of the device in a direction opposite to the direction of movement of the mobile equipment towards a communication state of the supply and evacuation ports, the housing being in communication permanent with the throat to bring the fluid and the element into contact.

In other words, it is expected that part of the pressure exerted on the transverse wall upstream of the throat is absorbed by the body by means of one or more mini-pistons that pass through the mobile equipment, in this way, the surface upstream of the throat is less than the surface downstream of the throat, it follows that the result of the forces due to the pressurized fluid applied to the mobile equipment is oriented in the direction of open communication between the feed and evacuation hole.

In one example, the device is a valve and the mobile equipment consists of only one piston. Thanks to the invention, the reduced force return means can be implemented because the force they are intended to oppose is reduced since it is proportional to the active surface of the element. Thus, when choosing an element that has a small active surface, the force applied by the pressure on the piston is reduced. The spring can then be reduced in size.

According to the invention, it is a distributor that consists of actuation means to communicate or not the supply port and the evacuation port independently of the pressure, for example, electromagnetic means, which allows to realize an electrovalve that offers sensitivity direct to fluid pressure. This direct sensitivity allows, for example, to make safer distributors, since they can allow a fluid to pass under pressure even in the event of failure of the drive means.

An object of the present invention, then, is a device for controlling the supply of fluid under pressure consisting of a body comprising an internal diameter of longitudinal axis, a mobile equipment suitable for sliding within the internal diameter, at least one orifice of feeding made on the body and arranged laterally with with respect to the longitudinal axis, at least one evacuation hole made in the body laterally with respect to the longitudinal axis, the mobile equipment being suitable to slide between at least a first position of interruption of communication between the supply hole and the evacuation hole and a second position of communication between the feeding hole and the evacuation hole, means for returning the mobile equipment to the first position, the mobile equipment comprising a lateral surface intended to cooperate with the internal diameter in a watertight or substantially at least one groove is watertight on the lateral surface of the mobile equipment, said groove being in permanent communication with the supply port, the mobile equipment consisting of at least one housing that extends parallel to the longitudinal axis and an element slidably mounted in said accommodation, said accommodation being in perm communication abutting said throat so that one end of said element is in contact with the pressurized fluid and where the element is fixed with respect to the body at least in a direction opposite to the direction of movement of the mobile equipment from the first position towards the second position.

In an exemplary embodiment, the mobile equipment may consist of several housings in permanent communication with said throat and a sliding element in each housing, so that one end of said elements is in contact with the fluid under pressure and where the elements are fixed with respect to the body at least in a direction opposite to the direction of movement of the mobile equipment from the first position to the second position.

The housing of the mobile equipment is, for example, coaxial to the longitudinal axis of the body.

In an exemplary embodiment, the mobile equipment is a piston consisting of the throat and at least one through longitudinal interior diameter where the element is slidably mounted, and where the second end of the element is mechanically abutted against a part lower body.

Another object of the present invention is a distributor consisting of a control device according to the invention and suitable external actuation means for moving the mobile equipment in the open position regardless of the pressure level in the throat.

The drive means consist of a magnetic core and a solenoid suitable for moving the magnetic core along the longitudinal axis.

The mobile unit consists of a distribution box that includes the throat and the magnetic core integral with the distribution box. The mobile equipment consists of a pusher between the distribution drawer and the magnetic core.

The housing is formed in the magnetic core and the distribution box and the pusher consist of a passage for supplying the pressurized fluid to the housing in the pusher.

Another object of the present invention is a hydraulic system consisting of a control device according to the invention or a distributor according to the invention.

Another subject of the present invention is a hydraulic pump consisting of a control device according to the invention or a distributor according to the invention.

Another subject of the present invention is a propulsion system for a motor vehicle consisting of a heat engine and a pump according to the invention.

Brief description of the drawings

The present invention will be better understood on the basis of the description that will follow and the attached drawings in which:

FIG. 1 is a sectional view of an embodiment of a hydraulic valve according to the invention in a closed state,

figure 2 is a longitudinal section view of the valve of figure 1 in an open state,

figure 3 is a sectional view of an embodiment variant of the hydraulic valve of figure 1 in a closed state,

figure 4 is a longitudinal section view of the valve of figure 3 in an open state,

FIG. 5 is a sectional view of an embodiment of a solenoid valve according to the invention in a closed state, the actuation means not being activated,

figure 6 is a longitudinal sectional view of the solenoid valve of figure 3 in an open state, the actuation means not being activated,

figure 7 is a sectional view of the solenoid valve of figure 5 in an open state, the actuation means being activated,

FIG. 8 is a sectional view of an embodiment variant of the embodiment of FIG. 5, in a closed state, the actuation means not being activated,

figure 9 is a longitudinal section view of the solenoid valve of figure 8 in an open state, not the drive means being activated,

figure 10 is a sectional view of the solenoid valve of figure 8 in an open state, the actuation means being activated,

FIG. 11 is a sectional view of an embodiment variant of the embodiment of FIG. 5, in an open state, the actuation means being activated or not.

Detailed exposition of particular embodiments

In Figures 1 and 2, an exemplary embodiment of a hydraulic valve according to the invention can be seen.

Hydraulic valve 2 can be mounted directly on the housing of a heat engine block or on an oil pump housing 1 of a heat engine for regulation of oil pressure in a heat engine or regulation of the pressure of any fluid .

The valve 2 consists of a body 4 intended to be mounted, for example, on a motor housing, a piston 6 or plug and a return means 8 that returns the piston 6 in the closed position of the valve.

The body has a longitudinal axis X and consists of an internal diameter 10 with a longitudinal axis X, where the piston 6, at least one lateral supply port 14 and at least one lateral evacuation port 16 are mounted in substantially watertight sliding, the two lateral holes 14 and 16 opening into the internal diameter 10 and being arranged in different longitudinal positions along the X axis.

The side feed port 14 is intended to connect to a source of pressurized fluid and the side discharge port 16 is intended to connect to a fluid feed system.

In the example shown, the body consists of two diametrically opposed feeding holes 14 and two diametrically opposite evacuation holes 16.

The inner diameter is closed at an upstream longitudinal end by a lower part 18 against which a longitudinal end 6.1 upstream of the piston is intended to abut. Upstream and downstream are considered with respect to the direction of piston displacement for valve opening, this direction being symbolized by arrow F.

The return means 8, which is in the represented example formed by a helical compression spring, is mounted in reaction between a downstream longitudinal end 20 of the internal diameter, opposite the lower part 18, and a downstream longitudinal end 6.2 of the piston opposite the longitudinal end upstream 6.1 of the piston.

In the example shown, the spring 8 is in abutment against a part 22 fixed on the internal diameter.

In the represented example, the valve consists of a vent 24 formed at the level of the longitudinal end downstream of the internal diameter 10 and the piston 6 consists of a longitudinal passage that extends over its entire length and ends at its upstream and downstream ends. and communicates with ventilation 24.

The piston consists on its outer lateral surface of an annular groove 26, which, in a closed state of the valve (Figure 1), is located in line with the supply opening 14.

The groove 26 is delimited longitudinally by an upstream end 28 and a downstream end 30. Advantageously, the groove 26 has a "stepped" shape that simplifies its implementation procedure. As a variant, the diameter of the lower part of the throat could be the same over the entire length of the throat.

The throat 26 has a certain axial extension so that, in the closed state, its downstream end is upstream of the evacuation opening, and in the open state, its upstream end is in line with the supply opening and its end downstream it is in line with the evacuation opening and connects the supply opening 14 and the evacuation opening 16.

The piston 6 consists of a housing 32 which extends parallel to the longitudinal axis and opens at the upstream end of the throat 26 and at the upstream longitudinal end of the piston, and an element 34 mounted movable in translation in the internal diameter so substantially watertight. Element 34 abuts permanently against the bottom of the inside diameter.

In this way, the pressurized fluid entering the feed port 14 in the throat 26 applies pressure on the throat walls and on a downstream longitudinal end 36 of the element 34.

The surfaces on which the fluid pressure is applied are equal to the projected surfaces of the throat walls on a plane perpendicular to the longitudinal axis.

The operation of the hydraulic valve according to the invention will now be described.

In the closed state represented in figure 1, the piston 6 is in a retracted position, its longitudinal end upstream abutting against the lower part of the internal diameter.

The fluid coming from the power supply enters the throat 26 through the supply port 14, its pressure is applied to the upstream 28 and downstream ends 30 of the throat 26. Due to the presence of the housing and the element 34 which is movable with respect to the piston 6 and abutting against the lower part of the internal diameter 4, the surface of the throat on which the pressure is exerted in the downstream and upper direction on which the pressure is exerted in the direction upstream and the resulting surface is equal to the surface of downstream end 36 of element 34. Therefore, there is a motive force exerted on the piston in the direction of the valve opening.

The fluid pressure that ensures valve opening depends on the feedback applied by the return means and the resulting surface. When the fluid pressure is sufficient, the piston moves according to arrow F, the downstream end of the throat 26 reaches in line with the evacuation holes 16 and connects the power supply and the system to be fed (figure 2 ). Communication between the system and the ventilation is interrupted.

Thanks to the invention, the spring load can be very low because it depends on the resulting surface on which the fluid pressure will be exerted, which corresponds to the cross section of the element 34, which may be weak. Accordingly, at a given opening pressure, the valve according to the invention implements a spring that has a lower load than the prior art valves, which enables smaller springs to be used and therefore saves space.

In addition, the valve is of simplified embodiment since the internal diameter of the body has a single diameter and the piston has a single external diameter, unlike prior art valves where the bore of the internal diameter of the body has at least two diameters in order to form a valve seat against which the piston engages to close the valve.

In the example of Figures 1 and 2, a single movable element with respect to the piston is implemented. As a variant, several movable elements can be mounted on the piston, for example distributed around the longitudinal axis.

Also, the movable elements could have different cross sections.

In Figures 3 and 4, a variant embodiment of the valve of Figures 1 and 2 is shown, where the element 34 and the internal diameter 32 are coaxial with the longitudinal axis X, in a closed state and an open state respectively .

The operation of the valve of Figures 3 and 4 is similar to that of the valve of Figures 1 and 2.

In the examples shown, the element 34 is independent of the valve body and abuts against it. In a variant, it can be considered to be integral with the lower part of the internal diameter, even if it is made in one piece with the lower part.

In the example shown, the longitudinal end of the element outcrops substantially with the upstream end ^{of the groove} 26 ^{, but it could be expected to fall back with respect to the upstream end, that is, the element} would have a length less than that of the internal diameter , or would protrude from the upstream end, that is, the element would be longer than the inside diameter.

The choice and section of the elements depend on the desired pressure threshold for the valve.

By way of example only, the diameter of the piston could have a diameter of 10 mm, and the diameter of element 34 could be between 0.5 mm and 3 mm.

In Figures 5 to 7, you can see an example of a drawer dispenser whose position is controlled by external actuation means. It may be a solenoid valve.

The solenoid valves of the prior art consist of a shutter, a magnetic core displaced by a magnetic field produced by a coil supplied with electric current causes the shutter to move and, therefore, it is put into communication between a fluid source and a system to feed. The opening of the solenoid valve is controlled only by the supply of the coil and in no case directly by the pressure applied on the plug.

On the contrary, the solenoid valve according to the invention has a certain sensitivity to the pressure of the fluid applied to the plug.

The solenoid valve consists of a body 104 and a piston or drawer 106 similar to the body 4 and piston 6 of the valve of figure 1, respectively. A return means 108 is provided between the body and the piston to return the piston to the piston closed position.

The body 104 consists of an internal diameter 110 with a longitudinal axis X, where the drawer 106 is mounted in a substantially watertight slide. It consists of at least one lateral feeding hole 114 and at least one lateral evacuation hole 116, leading to the two holes sides 114 and 116 on the inside diameter 110 and being arranged in different longitudinal positions along the X axis.

The side feed port 114 is intended to connect to a source of pressurized fluid and the side discharge port 116 is intended to connect to a fluid feed system.

In the example shown, body 104 consists of two diametrically opposed feed holes 114 and two diametrically opposed evacuation holes 116.

Inner diameter 110 is closed at an upstream longitudinal end by a core 138 to be described below.

The return means 108, which is in the represented example formed by a helical compression spring, is mounted in reaction between a downstream longitudinal end 120 of the inner diameter opposite the bottom 118 and a downstream longitudinal end 106.2 of the opposite drawer to the first longitudinal end 106.1 of the drawer. In the example shown, the spring is abutting against a piece 122 fixed on the inside diameter.

In the example shown, the valve consists of a ventilation 124 formed at the level of the second longitudinal end of the internal diameter 110 and the drawer 106 consists of a longitudinal passage that extends over its entire length and ends at its upstream and downstream ends and communicates with ventilation 124.

The drawer consists on its outer lateral surface of an annular groove 126, which in a closed state of the valve (Figure 5) is located in line with the supply opening 114.

The throat 126 is delimited longitudinally by an upstream end 128 and a downstream end 130. The throat 126 has a certain axial extension so that, in the closed state, its downstream end is upstream of the evacuation opening 116, and in the open state, its upstream end is in line with the feed opening 114 and its downstream end is in line with the evacuation opening 116 and communicates the feeding opening 114 and the evacuation opening 116.

The drawer 106 consists of a housing 132 that extends parallel to the longitudinal axis, leading to the upstream end of the groove 126 and the upstream longitudinal end of the drawer, and an element 134 mounted movable in translation on the inner diameter of a substantially watertight. Element 134 is permanently abutted against a magnetic sleeve 146 fixed with respect to body 104.

Thus, the pressurized fluid entering the feed port 114 into the throat 126 applies pressure to the throat walls and to a downstream longitudinal end 136 of the element 134 that is on the throat side.

The surfaces on which the fluid pressure is applied are equal to the projected surfaces of the throat walls on a plane perpendicular to the longitudinal axis.

Furthermore, the solenoid valve consists of actuating means 137 to control the flow of the fluid between the supply port 114 and the evacuation port 116. The actuating means 137 consists of a core 138 movably mounted on a solenoid 140 connected to a source of electric current, the solenoid being integrated in a magnetic loop 142 to guide the magnetic field and a pusher 144 arranged between the magnetic core and the longitudinal end upstream of the drawer 106, so that the displacement of the core 138 in the direction of the arrow F applies a pushing force to drawer 106 in the direction of opening of the solenoid valve. Solenoid 140 is, for example, a copper coil.

Magnetic sleeve 146 is fixed to body 104 and is assembled between drawer 106 and core 138, the latter is tightly mounted on body 104 and is pierced by pusher 144.

The drawer 106, the magnetic core 138 and the pusher 144 can be jointly in translation and form a mobile team. The drive means can be of any type, for example mechanical, piezoelectric ...

The operation of the solenoid valve is as follows:

Several figure cases can be presented:

a) The drive means 137 is not activated, which may result in a failure of the drive means or the power supply, for example.

The pressurized fluid fills the throat and applies a force to the upstream and downstream ends of the throat. As for the valve of Figures 1 and 2, the presence of the supporting element on the sleeve 146 that is fixed with respect to the body, the surface of the downstream end of the throat is greater than the upstream end of the throat. This active surface generates a force proportional to the pressure opposed to the load of the return spring that causes the drawer 106 to move. When the pressure is sufficient, the drawer 106 moves enough to bring the holes 114 into communication and 116. The communication between the system and the ventilation is interrupted (figure 6).

Thus, the solenoid valve has a certain direct sensitivity to the pressure level.

b) The control means 137 are activated. When the fluid pressure is insufficient to offset the spring load, the drawer is not displaced by the fluid. But due to the activation of the actuating means, the movable core 138 moves upstream towards downstream, pushes the pusher which itself pushes drawer 106. Drawer 106 then undergoes at the same time a pushing force exerted by the pusher and a pushing force exerted by the pressure of the fluid, when the total pushing force becomes greater than the spring load, the drawer 106 moves and puts the holes 114 and 116 in communication. The communication between the system and the ventilation it is interrupted (figure 7).

The displacement of the magnetic core 138 can be all or nothing or proportional to the current supplying the solenoid.

The fluid pressure necessary to allow ports 114 and 116 to communicate without activation of the drive means is chosen to be greater than the fluid pressure at which the drive means is programmed to put holes 114 and 116 in communication. In this way, the sensitivity of the solenoid valve to pressure ensures a safety function in case of failure of the solenoid valve.

As for the valve, various elements 134 could be mounted in the drawer.

In Figures 8 to 10, a variant embodiment of the distributor of Figures 5 and 6 can be seen.

In this variant embodiment, the pusher 244 and the drawer are in one piece and the pusher 244 is mounted on the movable core 238, the assembly forms a mobile equipment designated by reference 206 and slidably mounted on the magnetic sleeve 246.

The movable core 238 consists of a through passage 232 coaxial to the longitudinal axis X and where the element 234 is mounted. The mounting of the element 234 in the step 232 is such that the element can slide with respect to the core and that a seal is achieved. enough.

A piece 252 closes passage 232 at the upstream end side thereof which forms an axial stop for element 234. The drawer consists of a passage 250 extending between throat 226 and through passage 232 of core 238 downstream of the element 234 to allow pressurized fluid to contact face 236 downstream of element 234.

In the case where the fluid is motor oil, it being neither corrosive nor electrically conductive, the magnetic core 238 can be submerged in the motor oil. On the other hand, in the case of a corrosive and / or electrically conductive fluid, means are provided for sealing off the fluid core.

The upstream end of the piston is axially integral with the magnetic core 238, for example, it is adjusted to the force of the latter.

Advantageously, the central passage 232 consists of a reinforcement 254 located downstream of the element 234 and forming an axial stop for the element 234 in the downstream direction.

In this example, step 250 could have any shape, as it only serves to bring the pressurized fluid into contact with element 234.

The operation of this variant is as follows:

In figure 8, the control means 237 are not activated and the pressure in the throat 226 is less than that which allows to overcome the spring load, the distributor is closed, the supply 214 and evacuation holes 216 are not in communication .

When the control means 237 are not activated and the fluid pressure is sufficient to counteract the load of the return spring, the element 234 comes to a stop against the part 252, it cannot move, the mobile equipment stops. displaces proportionally to the pressure against the return spring. The feed port 214 and the evacuation port 216 are brought into communication. The communication between the evacuation port 216 and the ventilation is closed (figure 9).

Therefore, the distributor changes state without activation of the control means.

When the control means are activated and that is, when the solenoid is supplied with current in the example shown, and the fluid pressure is insufficient to counteract the spring return force, the mobile equipment moves upstream towards waters down. When the force applied by the mobile equipment and the force applied by the hydraulic pressure are greater than the spring return force, the feeding hole 214 and the evacuation hole 216 are put into communication and the communication between the evacuation hole 216 and the ventilation is interrupted (figure 10).

This variant has the advantage of being simple and simple to carry out.

In figure 11, another variant embodiment of the distributor of figure 8 can be seen, where the length of the pusher, which is in one piece with drawer 206, is such that element 234 slides directly in step 250 running longitudinally through the drawer. For simplicity of implementation, the passage 250 extends longitudinally along the X axis, but it could be envisaged that only the portion of the passage 250 that houses the element 234 is rectilinear to allow its sliding. The distributor is in an open state, the actuation means being activated or not.

This variant has the advantage of being simple and simple to carry out.

In the examples described, these are three-way distributors, but it will be understood that a distributor with a greater number of routes does not depart from the context of the present invention.

The distributor according to the invention can be very advantageously implemented in any system for regulating a pressure of a fluid, for example, in an oil pump of a thermal engine to regulate the oil pressure in the engine.

Thanks to the invention, the control devices for the supply of fluid under pressure can be made with a simplified structure because the internal diameter of the body can consist of a single diameter and the outer surface can consist of a single diameter.

In addition, in the case of distributors, they offer pressure sensitivity, which makes it possible to have supply systems with increased safety without having to resort to other devices, such as an additional regulating valve.

Claims (6)

1. Distributor consisting of a device for controlling the supply of fluid under pressure, consisting of a body comprising an internal diameter of the longitudinal axis (X), a mobile equipment (206) suitable for sliding within the internal diameter, when minus a supply hole (214) made in the body and arranged laterally with respect to the longitudinal axis (X), at least one evacuation hole (216) made in the body laterally with respect to the longitudinal axis (X), the equipment being mobile (206) suitable for sliding between at least a first communication interruption position between the supply port (214) and the evacuation port (216) and a second communication position between the supply port (214) and the evacuation hole (216), means for returning the mobile equipment to the first position, the mobile equipment (206) comprising a lateral surface intended to cooperate with the internal diameter of m Airtight or substantially watertight, at least one groove (226) on the lateral surface of the mobile equipment (206), said groove (226) being in permanent communication with the supply port (214), the mobile equipment (206) consisting of at least one housing (232) extending parallel to the longitudinal axis (X) and of an element (234) slidably mounted on said housing (232), said housing (232) being in permanent communication with said groove (226) such that one end of said element (234) is in contact with the fluid under pressure and where the element (234) is fixed with respect to the body at least in a direction opposite to the direction of movement of the mobile equipment (226) of the first position towards the second position, said distributor also consisting of external actuation means (237) suitable for moving the mobile equipment (206) to an open position regardless of the pressure level in the throat (226), with said actuation means (237) being a magnetic core (238) and a solenoid (240) suitable for moving the magnetic core (238) along the longitudinal axis (X), where the mobile equipment consists of a drawer of distribution (206) comprising the throat (226), a pusher (244) and the magnetic core (238), the pusher (244) being in one piece with the distribution drawer (206) and being arranged between the drawer of distribution (206) and the magnetic core (238), said magnetic core (238) being axially integral with the distribution box (206), where the housing is formed in the magnetic core (238) and where the distribution box (206) and pusher (244) consist of a passage (250) for supplying the pressurized fluid to the housing (232) in the magnetic core (238). 2. Distributor according to claim 1, wherein the mobile equipment (206) consists of several housings (232) in permanent communication with said groove (226) and a sliding element in each housing (232), so that one end of said elements (234) are in contact with the fluid under pressure and where the elements (234) are fixed with respect to the body at least in a direction opposite to the direction of movement of the mobile equipment (206) from the first position towards the second position. 3. Distributor of claims 1 or 2, wherein a housing of the mobile equipment (206) is coaxial to the longitudinal axis of the body. 4. Hydraulic system consisting of a distributor according to one of claims 1 to 3. 5. Hydraulic pump consisting of a distributor according to one of claims 1 to 3. 6. A propulsion system for a motor vehicle consisting of a heat engine and a pump according to claim 5.